WO2008018149A1 - Mécanisme de limitation de couple - Google Patents

Mécanisme de limitation de couple Download PDF

Info

Publication number
WO2008018149A1
WO2008018149A1 PCT/JP2006/315966 JP2006315966W WO2008018149A1 WO 2008018149 A1 WO2008018149 A1 WO 2008018149A1 JP 2006315966 W JP2006315966 W JP 2006315966W WO 2008018149 A1 WO2008018149 A1 WO 2008018149A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque
friction
contact position
ball
input
Prior art date
Application number
PCT/JP2006/315966
Other languages
English (en)
Japanese (ja)
Inventor
Hiroaki Murakami
Original Assignee
Shimadzu Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shimadzu Corporation filed Critical Shimadzu Corporation
Priority to PCT/JP2006/315966 priority Critical patent/WO2008018149A1/fr
Priority to US12/373,422 priority patent/US8105171B2/en
Publication of WO2008018149A1 publication Critical patent/WO2008018149A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
    • F16D7/027—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs with multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
    • F16D43/213—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces
    • F16D43/215—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces with flat friction surfaces, e.g. discs
    • F16D43/216—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces with flat friction surfaces, e.g. discs with multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

  • the present invention relates to a power transmission system of an aircraft, a general industrial machine, etc., and relates to a torque limiting mechanism that suppresses transmission when excessive input torque is applied.
  • a slip clutch (see, for example, the following patent document) is well known as a mechanism capable of suppressing torque transmission when excessive input torque is applied while transmitting torque from the input shaft to the output shaft. .
  • a slip clutch transmits torque through friction between a friction plate that is splined to the input shaft and a friction plate that is splined to the output shaft, and slips the friction plates when excessive input torque is applied. This suppresses the transmission torque.
  • the output torque should be surely limited to a desired specified value or less depending on the instability of the friction coefficient and the operating conditions. There is a problem that is difficult. In particular, it cannot be denied that a surge or overshoot phenomenon that causes the output torque to exceed the specified value occurs before and after the occurrence of slip.
  • the present invention made in view of the above is intended to realize a highly accurate torque limiting mechanism capable of limiting the output torque to a specified value or less, and to reduce the friction torque when a slip occurs.
  • the purpose is intended to realize a highly accurate torque limiting mechanism capable of limiting the output torque to a specified value or less, and to reduce the friction torque when a slip occurs. The purpose.
  • Patent Document 1 Specification of # 112005-327332
  • Patent Document 2 Japanese Patent Laid-Open No. 2002-031156
  • a ball ramp portion is provided together with a torque limiting mechanism in which a slip clutch portion is interposed between an input shaft and an output shaft, and at least part of the input torque is transferred to the ball ramp portion.
  • the friction between the friction plates constituting the slip clutch portion can be reduced by utilizing the axial thrust generated in the ball ramp portion according to the magnitude of the torque transmitted to one cam element.
  • the friction plates constituting the slip clutch are elastically biased so as to press each other.
  • the ball ramp When the input torque exceeds the specified limit, the ball ramp generates an axial thrust of the required size and counteracts the elastic urging force with the axial thrust to reduce the friction torque of the friction plate. .
  • first contact position and the second contact position are set on the inner surface of the concave portion of the cam element of the ball ramp portion, and the ball comes into contact with the first contact as the relative rotation of both cam elements proceeds.
  • Positional force Assuming that it reaches the second contact position, the acute angle between the surface perpendicular to the axis of the contact surface with respect to the ball at the second contact position is the axis of the contact surface at the first contact position.
  • the inner surface of the recess was formed so as to be smaller than the acute angle formed with the surface orthogonal to the surface. Slip is generated in the slip clutch when the torque transmitted to the friction plate exceeds the friction torque of the friction plate. The increase in the torque transmitted to the friction plate also increases the friction torque of the friction plate.
  • both decreases are caused by an increase in input torque to the input shaft. Therefore, even if the operation of the ball ramp is started when the specified input torque is applied, i.e., both cam elements are separated and the axial thrust is exerted, the friction torque is further increased. However, it is possible that slip will occur with higher friction torque than expected. In other words, an output torque exceeding the specified value is transmitted to the output shaft.
  • the shape of the inner surface of the recess of the cam element particularly the inclination angle of the contact surface where the inner surface of the recess contacts the ball, determines the relationship between the amount of increase in input torque and the amount of increase in axial thrust.
  • FIG. 1 is an end view showing a torque limiting mechanism according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of a main part showing a ball ramp portion of the torque limiting mechanism.
  • FIG. 3 is a partially enlarged view of FIG.
  • FIG. 4 is a graph showing the relationship between friction torque, input torque, and displacement of the float block.
  • the torque limiting mechanism of the present embodiment is provided between an input shaft (or output shaft) 1 and an output shaft (or input shaft) 2 that are driven to rotate about the same axis A.
  • the slip clutch 3 is interposed between the two and the two are connected to transmit the torque input to the input shaft 1 to the output shaft 2.
  • the input shaft 1 includes an input shaft main body 11, an input side rotor member 12 driven by the input shaft main body 11, and a ball ramp portion 13 interposed between the input shaft main body 11 and the rotor member 12.
  • the opening member 12 can be displaced in the direction of the axis A independently of the input shaft body 11 and can be rotated around the axis A.
  • the ball ramp portion 13 includes cam elements 131 and 132 that are paired along the axis A direction, and a ball 133 that is sandwiched in a recess (concave groove) G formed in both cam elements 131 and 132.
  • one cam element 131 is fixed to a predetermined portion of the input shaft main body 11 in a radially extending manner, and the outer periphery of the rotor member 12 is arranged so that the other cam element 132 faces the one cam element 131.
  • Spline join key join
  • the other cam element 132 is not displaced relative to the rotor member 12.
  • the slip clutch section 3 includes a friction plate 31 on the input shaft 1 side, a friction plate 32 on the output shaft 2 side, and elastic urging means 33 that presses the friction plates 31 and 32 in the direction of the axis A.
  • the input-side rotor member 12 is accommodated in the output shaft 2
  • the friction plate 31 is connected to the outer periphery of the rotor member 12
  • the friction plate 32 is connected to the inner periphery of the output shaft 2, respectively. It overlaps alternately along the direction of heart A.
  • the elastic urging means 33 includes a push block 331 for pressing the friction plates 31 and 32 from one side, a float block 332 for pressing the friction plates 31 and 32 from the other side, and the float block 332 toward the push block 331.
  • the preload spring 333 which is elastically biased, and the float block 332 (or push block 331) and the friction plate 31, 32, the friction plates 31, 32 are pushed into the push block 331 (or float block 332).
  • the preload spring 333 also serves as means for elastically urging the rotor member 12 and the other cam element 132 toward the one cam element 131 via the float block 332.
  • the inner surface shape of the recess G formed in both the cam elements 131 and 132 of the ball ramp portion 13 is improved to improve the accuracy of the transmission torque limitation.
  • the shape of the inner surface of the recess G is shown in FIGS.
  • the inner side surfaces formed in the recesses G of the cam elements 131 and 132 are continuous surfaces having a plurality of contact positions Gl and G2 with respect to the ball 133.
  • the ball 133 is in contact with the vicinity of the first contact position G1.
  • a phase difference in the rotational direction occurs between the other cam element 1 32 and one cam element 131,
  • the other cam element 132 is displaced away from the other cam element 131.
  • the contact position of the ball 133 at this time depends on the magnitude of the input torque transmitted to one cam element 131, and the force in the vicinity of the first contact position G1 is also directed to the vicinity of the second contact position G2 and further away from it. Move gradually with force.
  • ⁇ is the inner surface of the recess G
  • the contact surface S with respect to the rail 133 is an inclination angle (acute angle) formed with the virtual surface B perpendicular to the axis A. Since the cam element 132 is elastically biased by the preload spring 333, the displacement amount of the cam element 132, the input side rotor member 12, and consequently the float block 332 in the axial center A direction is substantially proportional to the axial thrust F. If the torque T is constant, the amount of displacement of the float block 332 in the axis A direction is approximately proportional to the inclination angle ⁇ of the contact surface S.
  • the inner side surface of the recess G is formed such that the inclination angle of the contact surface at the second contact position G2 is smaller than the inclination angle of the contact surface at the first contact position G1. ing. Power!
  • the surface portion from the first contact position G1 to the second contact position G2 is curved so that the inclination angle decreases.
  • the surface portion far from the second contact position G2 is, for example, an inclined surface that is substantially equal to the inclination angle of the second contact position G2.
  • the relationship X between the displacement amount of the float block 332 in the axial center A direction and the friction torque of the friction plates 31 and 32, and the relationship Y between the displacement amount of the float block 332 and the input torque that causes the displacement are illustrated in FIG. Shown in 4.
  • the friction torque of the friction plates 31 and 32 is approximately inversely proportional to the displacement amount of the float block 332.
  • the slip of the friction plates 31 and 32 occurs when the input torque exceeds the friction torque, that is, at the intersection of the graph X and the graph Y in FIG. 4, and the magnitude of the input torque when the slip occurs is Ys, friction torque is Xs.
  • the torque transmitted from the input shaft 1 to the output shaft 2 can be reliably limited to a predetermined value or less, and the friction torque of the friction plates 31 and 32 when a slip occurs can be reduced. It becomes possible to decrease.
  • the inner side surface of the concave portion of the ball lamp conventionally known is exclusively an inclined surface having a constant inclination angle.
  • the input torque must be increased as shown by the graph Z in FIG. Therefore, excessive torque exceeding the specified value will be transmitted. It cannot be denied, and the friction torque at the time of slip must be increased.
  • the present invention is not limited to the embodiment described in detail above.
  • the shape of the inner surface of the recess G of the cam elements 131 and 132 is not limited to the illustrated example.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un mécanisme de limitation de couple de grande précision qui peut limiter le couple de sortie à un niveau ne dépassant pas une valeur spécifiée, et dans lequel un couple de frottement est réduit lorsqu'il se produit un frottement. Une partie rampe (13) de roulement à billes est prévue au niveau d'une section de limiteur de couple à friction (3) constituée de plaques de frottement (31, 32). Une force de poussée axiale qui dépend de la grandeur du couple d'entrée est produite au niveau de la section (3) rampe à billes. Le frottement entre les plaques de frottement (31, 32) est réduit en utilisant cette force de poussée axiale pour limiter le couple de transmission. En outre, la forme des surfaces intérieures d'évidements (G) formés dans des éléments de came (131, 132) de la section de rampe à billes (13) est améliorée pour augmenter la précision de la limitation du couple de transmission.
PCT/JP2006/315966 2006-08-11 2006-08-11 Mécanisme de limitation de couple WO2008018149A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2006/315966 WO2008018149A1 (fr) 2006-08-11 2006-08-11 Mécanisme de limitation de couple
US12/373,422 US8105171B2 (en) 2006-08-11 2006-08-11 Torque limiting mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2006/315966 WO2008018149A1 (fr) 2006-08-11 2006-08-11 Mécanisme de limitation de couple

Publications (1)

Publication Number Publication Date
WO2008018149A1 true WO2008018149A1 (fr) 2008-02-14

Family

ID=39032694

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/315966 WO2008018149A1 (fr) 2006-08-11 2006-08-11 Mécanisme de limitation de couple

Country Status (2)

Country Link
US (1) US8105171B2 (fr)
WO (1) WO2008018149A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110308906A1 (en) * 2009-04-06 2011-12-22 Messier-Bugatti-Dowty Mechanical device for the transmission of a force with a threshold
CN114569037A (zh) * 2022-03-21 2022-06-03 江苏凯德电控科技有限公司 一种开门装置及安装开门装置的洗碗机

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8307731B2 (en) * 2006-11-30 2012-11-13 Magna Powertrain Usa, Inc. Torque limiting shaft and sprocket assembly
KR102038162B1 (ko) * 2011-11-16 2019-10-29 알리손 트랜스미션, 인크. 입력 댐퍼 내의 제한적 토크 클러치
US9446908B2 (en) 2012-02-05 2016-09-20 Matthews Resources, Inc. Conveying systems and methods of associating data with an item transported by a conveying system
US10130799B2 (en) 2014-08-27 2018-11-20 Acclarent, Inc. Inflator with varying mechanical advantage
US10066683B2 (en) * 2015-04-10 2018-09-04 Goodrich Corporation Clutch for a winch
US9988249B2 (en) * 2015-05-19 2018-06-05 Goodrich Corporation Clutch for a winch or hoist
CN105782267B (zh) * 2016-05-09 2017-11-03 黄山奔马集团有限公司 一种分体多片式离合器总成
CN105805278B (zh) * 2016-05-09 2018-10-30 黄山奔马集团有限公司 一种电动车用分体式自适应自动增矩节能驱动总成
BE1025046B1 (nl) * 2017-03-10 2018-10-11 Cnh Industrial Belgium Nv Slipkoppeling voor een werkmachine
DE102017120530A1 (de) * 2017-09-06 2019-03-07 Schaeffler Technologies AG & Co. KG Rutschkupplung mit einer Rotationsachse
CN115030966B (zh) * 2022-04-18 2023-08-01 天津君亚沃德科技发展有限公司 摩擦联结器及转辙机

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* Cited by examiner, † Cited by third party
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JP2005133775A (ja) * 2003-10-29 2005-05-26 Shimadzu Corp トルクリミッタ
JP2006177382A (ja) * 2004-12-20 2006-07-06 Shimadzu Corp トルク制限装置

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US3511349A (en) * 1968-08-30 1970-05-12 Deere & Co Clutch
CA1166482A (fr) * 1980-12-08 1984-05-01 Masao Hiruma Dispositif amotisseur de vibrations torsionnelles
US5031746A (en) * 1990-03-30 1991-07-16 Erkki Koivunen Multi-mode clutch for change-speed transmissions
JP2002031156A (ja) 2000-07-17 2002-01-31 Mitsubishi Heavy Ind Ltd ブレードスリップクラッチ
US6568519B2 (en) * 2001-08-10 2003-05-27 Borgwarner, Inc. Torque limiting chain sprocket assembly
JP4483412B2 (ja) * 2003-10-22 2010-06-16 株式会社島津製作所 トルクリミッタ
JP2005327332A (ja) 2004-05-12 2005-11-24 Fuji Photo Film Co Ltd テープの貼付装置および貼付方法
US7377871B2 (en) * 2006-03-27 2008-05-27 Magna Powertrain Usa, Inc. Transfer case with torque limiting clutch assembly

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005133775A (ja) * 2003-10-29 2005-05-26 Shimadzu Corp トルクリミッタ
JP2006177382A (ja) * 2004-12-20 2006-07-06 Shimadzu Corp トルク制限装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110308906A1 (en) * 2009-04-06 2011-12-22 Messier-Bugatti-Dowty Mechanical device for the transmission of a force with a threshold
US8789672B2 (en) * 2009-04-06 2014-07-29 Messier-Bugatti-Dowty Mechanical device for the transmission of a force with a threshold
CN114569037A (zh) * 2022-03-21 2022-06-03 江苏凯德电控科技有限公司 一种开门装置及安装开门装置的洗碗机

Also Published As

Publication number Publication date
US8105171B2 (en) 2012-01-31
US20090301836A1 (en) 2009-12-10

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